Hydraulic clutch and brake mechanism



Feb. 20, 1940. M. KEssLER HYDRAULIC vCLUTCH AND BRAKE MECHANISM Filed May 10, 1957 3 Sheets-Sheet 1 fill! NRT//v KESSLER INVENTOR ATTORNEY Feb. 20, 1940. M. KL-:ssLER HYDRAULIC CLUTCH AND BRAKE MECHANISM Filed May l0, 1957 3 Sheets-Sheet 2 NVENTOR BY ATTORNEY Feb. 20, 1940. M, KEssLER HYDRAULIC CLUTCH AND BRAKE MECHANISM Filed May 10, 1937 PIE-10 MHRT/N KESSLEI? INVENTOR ATTORNEY Patented Feb. Z0, 1940 UNITED i STATES- Martin Kessler,

AND BRAKE Mirella-r sM Y Cleveland, Ohio Application May 10, 1937, Serial No. 141,658

Claims.

This application which is a continuation in part of my pending application Ser. '710.671, led Jan. 7, 1935, relates to improvements in hydraulic clutch and brake mechanism adapted to be used for power presses, wire draw benches and other power driven machines embodying continuously driven iiywheels' and coupling means for energy from the'iiywheel at irregular intervals to the driven parts of these machines. The invention has for its general object the provision of hydraulic clutch and brake mechanismhaving a. clutch member and a `brake member, each of which members circulates fluid in an endless, valved passage arranged in the respective member-and generates clutching and/or braking power by -controlling in the respective passage. l

Another object of the invention is the provision of hydraulic clutch and brake mechanism with a central valve memberl secured to the driven shaft'of a power driven machine, and a piston supporting member secured to -the continuously rotating flywheel of said machine, the piston supporting member being intersleeved with the valved member for forming an endlesspassage including the valved portion of the valved member.

A further object of the invention is the provision of a hydraulic clutch and brake mechanism for power driven machines embodying a clutch member anda brake member, each of the two members embodying inner and outer members intersleeved with each other for forming endless passages circulating fluid in their respective channels and being arranged side by side `with their` inner members secured to the driven' shaft of the machine and their outer members secured to the flywheel of the machine and to a-'stationary part thereof respectively, so as to eiect` coupling action between the driven shaft andthe flywheel and braking action on said shaft, when the flow of a fluid in the endless channels ofthe clutch and/or the brake is retarded or stopped: by operation `of the valves controlling the respective channels.

Still another object ofthe invention is the. provision; of hydraulic clutch and brake mechanism of the type referred to above, wherein the outer members ofthe clutch andbrake yieldingly support shiftable piston members co-operating `with spring-pressed plunger-like means in said outer members for counteracting centrifugal forces onsaidpistons', when said outer members rotate aty high velocities and for shockabsorbing action ofV said pistons, when the flow the flow of .,uid

(Cl. IBR- 12) of liquid in the and brake is instantaneously stopped den closing of the respective valves.

With these and incidental objects in view, the invention consists novel features of in certain construction and combination of parts, the essential elements of which are set forth in the appended claims; and a preferred form of endless passages of said'clutch by too sudembodiment of the invention is hereinafter shown with reference to the drawings accompanying and forming part of this speciiication.

In the drawings:

Fig. 1 is a transversal sectional a hydraulic clutch and brake mechanism according to the invention attached to and coupled with the flywheel and driven shaft of a power driven machine, such as a power press;

I Fig. 2 is a transversal sectional view through the clutch member cf the clutch and brake mechanism shown in Fig. 1, the section being taken on line 2-2 of Fig. 1;

Fig. 3 is a. transversal sectional view through the brake member of the clutch and brake mechanism shown in Fig. 1, the section lbeing takenv on line 3-3 of Fig. 1;

Fig. 4 is a cross sectional view through one of the pistons of the clutch member, the section being taken on line 4-4 of Fig. 2;

Fig. 5 is a diagrammatical mechanism actuating the valve arrangement. of the clutch and brake mechanism for operating the clutch member, the vi'ew being taken on line 5-5 of Fig. 1: Y

Fig. 6 is a diagrammatical view ofthe cam mechanism actuating the valve arrangement of the clutch and bra `e mechanism for operating the brake member, line 6-6 of Fig. 1;

Fig. I is a transversal sectional view through a somewhat modified fluid brake mechanism accordingto the invention applied to the wheel of a vehicle, the section being taken on vline 1-1 of Fig. 8;

Fig. 8 is a longitudinal sectional view through the fluid brake shown in Fig. "I, the section being taken on line 8-8 of Fig. '1; f

Fig. 9 is a fragmentary sectional View on line 9-9 of Fig. 8, showing the cross-section of one of the pistons and the grooves for guiding the piston in the outer rotary me ber of the uid brake;

Fig. 10 is'a sectional view cn line Ill- I Fig. 11 is a section of the fiuid'brake shown the View being taken on view through view of the cam ing the relief check valve which controls the relief passage for iiuid which has seeped into the piston chamber, the section being takenv on nels I1, I1 and valve chamber I8,

.fis

through, so that line II--II of Fig. 8.

Referring now to Figs. V1 through 6 reference numeral 2 denotes a shaft supported in bearings 3 and 4, which .shaft is coupled with the crank shaft of a power press, not shown, by means of gears 5 and 6 and has freely rotatably arranged thereon a iiywheel 1 driven in any suitable manner. Flywheel 1 by means of cap screws 9 is secured to the rotary outer member 9 of a hydraullc clutch I9, the inner member II of which is keyed to the shaft 2 and consequently the flywheel transmits its rotary energy to the shaft 2, when the clutch I9 is actuated.

Inner member II of clutch I 9, which member rotatably supports outer member 9, consists of a substantially cylindrically shaped body I2 with an eccentric keyed bore I4. to permit of the body I2 being eccentrically sleeved upon shaft 2 and secured to said shaft by means of a key I5. The body I2 furthermore is provided at its opposite sides with circular shoulders I8' arranged concentrically with respect to bore I4, which shoulders guide the outer member 9 and effect concentric'rotatlon of said member around bore I4 and shaft 2. In addition, body I2 is provided with oppositely arranged channels I1, I1' respectively, separated by a valve chamber I8, which valve chamber has rotatably secured therein a valve I9 for restricting or fully closing communication between the opposedchannels I1, I1'.

The thus formed -inner member I'I rotatably supports the. outer member 9 upon the circular shoulders I8', which member 9 consists of a substantially ring-shaped hollow body 29, having at opposite sides inwardly extending flanges 2l, riding upon the shoulders I8' above'referred to. Body 29 is made of a base portion 22, having laterally extending therefrom a circular flange 23 to'facllitate attachment of said portion to the flywheel 1 by the cap screws 8, and a plate-like portion' 24 secured to said base portion by cap screws 25, so as to permit of the body 29 being readily sleeved upon the shoulders I8' of the inner member II.l

'The inner and outer members of theclutch being arranged eccentrically with lrespect to each .other form a crescent-shaped chamber 26, the

narrowed opposite ends 21, 21' of which are in communication with each other through chanand this chamber is' subdivided 4by spring-pressed abutment blades 28 slidably mounted in slots 29 in the inner wall 39 of outer member 9, which blades Iare yieldably forced into contact vwith the periphery of the body I2 of the innermember II'. Any liquid within chamber 26 will be carried around by -blades 28 when the outer member 9 is rotated with respect to the inner member I I and such rotation is controlled by the valve I9 in valve chamber I8, as all liquid must pass through thisvalve. Consequently, when the valve I 9 is in a fully open position, then the liquid freely passes through the valve and thenl the outer member I2 can freely rotate, and when the valve is partly or fully closed, then the liquid is forced through said valve or rotation of member I2 is retarded or entirely prevented,"as the case may be.

Y As abutmeni'f-blades'128.A are yieldingly forced into 'contact Awith the ,periphery of the inner member I I by means of light' springs 39' -centrifugal forces at higher speeds lofthe outer member prevented from passing therecylinders communicate with chamber 26 through narrow bores 35 and further embody central bores 39 having check valves 31 arranged there.- in. When member 9 is rotated at higher speeds' then centrifugal forces on plungers 3l shift same outwardly, eifect a compression of the "liquid within the ring-shaped chamber 38 of the body 29. thereby press upon the exposed outer faces 39 of the abutment blades 28 and thus counteract centrifugalforces on said abutment blades. In addition, plungers 3| provide shock-absorbing means counteracting danger of breakage by too sudden closing of the controlling valve I 9 and thereby insure smooth gripping action of the clutch.

In power driven machines it is necessary that operation of the machine is quickly stopped from further rotation as soon as the clutch is released. Such action is effected by a brake mechanism 49 of similar construction which iscoupled with the clutch I9. This brake mechanism embodies inner and outer members 4I, 42 respectively, similar in construction but narrower in width than the inner and outer members 9 and II of the clutch, Vtherefore detailed description of members 4I, 42 is deemed to be superuous. However, member 42 is rigidly secured to the bearing Y4 of shaft 2, cap screws 42' being used to attach vmember 42 to bracket-like extension means 43 on bearing 4.v

Clutch I9 and brake mechanism 49 are adapted to cooperate. Thus, when the clutch is thrown in, then the brake is automatically released and vice versa. This co-operation of the two elements is effected by cams 44 and 45, cam 44 being secured to outer member 9 of clutch I9, and cam*YV 45 being secured to brake member 42, which cams act upon the rollers 46 of a lever 46 slidably but non-rotatably secured to a shaft 41 coupled with the valve I9 for the clutch and the valve I9 for the4 brake, the valve being of course adjusted, so that valve I9 is fully closed when valve I9' is opened and vice versa. A shifting of the lever 46 on the shaft 41 is effected by a spring 48 and a solenoid 49, which latter, when energized, effects shifting of said lever into engagement with the cam 44 and therewith throwing in of the clutch by means of 1a. bell crank 59,

a collar 5I on shaftA 2, and two symmetrically arranged push rods' 52 secured to collar 5I and having their ends connected by a coupling plate 53, and which. when de-energized, permits -of 41 against the yielding force ofv spring 49 toward cam 44. 'I'hen the cam 44 vcauses lever49 ,to

be moved in such a fashion that shaft 41 will be rotated, so that valve I9 will be closed and valve I9 will be opened. Closing of valve I8 effects vcoupling of the rotary outer member 9 of clutch I0 .with the inner member II so that ilywheel 1 is coupled with shaft 2, and opening of valve I9' effects release of the coupling between the members 4I and 42 of the brake mechanism and therewith releases the braking action of said mechanism. The valves I9 and I9' remain in their closed and opened positions until the solenoid 49 is deenergized and the yielding force of spring 48 shifts lever 46 on shaft 41 toward cam 45. This cam, being secured to brake member 42, is stationary, and effects shifting of lever 46, which lever rotates with the inner member 4I, so that shaft 41 will be axially rotated in a direction effecting opening of valve I9 and closing of valve I9.' lSuch actuation of the valves effects release of the coupling of the members 9 and II of the clutch and coupling of the members 4I and 42 `of the brake mechanism, so that the clutch is released and the brake mechanism is energized.

In Figs. 7 to 11 I have illustrated a somewhat modified form of a fluid brake attached to the rear axle housing of an automobile, which housing supports an axle 58 in its cylindrically enlarged end portion 64 by means of anti-friction roller bearings 65. A perforated end plate 66 permits of the housing being filled with a lubricant. The outer endV 68 of the axle 63, which end extends through the plate 66, is keyed to a wheel 69 by means of a key 10. This wheel is provided with a cup-shaped, flanged disk 1I, the flange 12 of which seats a ring-shaped member 14 having substantially angular cross section and is integrally formed with an L-shaped flange 15 opposite the ange .12' of disk 1I for rigid connection therewith by means of bolts 16.

The member 14 forms the body of a member A, is rotatably engaged with a cylindrical member B, rigidly mounted on housing 62 by bolts 18, which bolts extend through perforations in an internal circumferential ange 80 on housing 62. Member B embodies a central, raised circular portion 82 of larger diameter than the adjoining outer circular portions 83, 83' of said member and is axially offset with respect tothe axis of member A and the wheel so as to contact.

at 85 with the inner wall 84 of the ring-shaped member 14. Circular portion 82 of member B channels 86 and passages is partially grooved at lopposite sides of its con- "ftact point with the wall 84 to form substantially symmetrically arranged channels 86. These channels communicate by means of symmetrically arranged passages 88 with a valve chamberv 81 in member B opposite the contact point 85, which chamber has rotatably mounted'therein a valve cock 91.

The circular end portions 83, 83' of cylindrical member B extend at opposite sides through a member A, thewall 90 of which abuts the circular portion 82 of member B, so as to form therewith a circular 'channel or fluid passage C, the opposite wall of which is formed by a perforated ring-shaped and flanged cover vplate 9I. This cover plate is sleeved upon the circular end portion 83 of member B and abuts' the opposite side of the circular portion 82.

The passage C, which,` asrpreviously described. communicates with valve chamber 81 through V88, is of .orbital form and permits ofI a brake'. `iiuid, air, oil or water meets no kresistance being freely circulated therein. The circulation of the fluid is controlled by the valve cock| 91 of the valve chamber 81. 'Ihis valve cock is rotatably mounted and held in proper working position by means of a compression spring 98. 5

The brake fluid is circulated in passage C by slidable spring pressed abutments or pistons |02, carried by symmetrically arranged bosses |08, integrally formed on the member 14.

When the member A is rotated in the direction 10 of arrow |04 (see Fig. 7) and the cock 91 is held in its fully opened position by actuating operating nlever |05, then'the pistons |02 carry the brake ,fluid successively from one side of passage C through the valve chamber 81 to the other side 15 and hence back to the first `side of passage C and so forth. Such circulation'of thebrake uid with a fully opened valve position and therefore the fluid circulates freely, however, when the lever |05 rotates the cock 91 to partly closed position, then the brake fluid must be forced through a small passage and meets substantial l resistance when' passing through the partly closed valve chamber 81. This resistance against the circulation of the fluid generates a counter or braking power, which tends to stop rotation of the piston carrying member I4 and the wheel connected therewith. The developedbraking power depends entirely upon tht size of the passage through the partly closed valve chamber 81 and becomes infinite when valve chamber 81 is fully closed. In the latter instance the rotary member A and the stationary member B are tightly coupled with each other, as the nula body is forced against 35 a solid wall and prevents rotation of the member A.

The pistons |02 when riding upon member B reciprocate in their cylinders. Each of these pistons, when the cock 91 is actuated and sudo denly acts asa shock absorbing element, restricts the circulation of lthe fluid, in which case the piston counteracts the braking power and prevents breakage of parts, should the valve chamber a1 be dosed too abrupuy'. This timely shock 45 absorbing action of the piston members is possible on account of the grooves or channels 88,` which channels permit of pressure being exerted upon the bottom face of the pistons for effecting yielding movement of the pistons against the 50 tension of the springs |06.

, Having thus described my claim is:

l. In a hydraulic clutch and brake mechanism la rotary shaft, rotary driving means, a hydraulic 55 clutch member adapted t@4 couple said rotary driving means with said shaft, a hydraulic brake member adapted to brake said shaft when not coupled with said rotary driving means, and a single controlling means for said clutch member 60 and said brakemember, said clutch and brake members each embodying an inner member rigidly coupled with saidlrotary shaft, said clutch member embodying a rotary outer member riginvention, what I idly coupledl with'said rotary driving means, and 65 bers, secured in aligned and spaced relation to 70v said shaft, each of said members embodying a cross passageand a valve controlling said passage,`a ring-shaped member foreach of said circular members eccentrically encircling same and .forming'an endless fluid channel including said 75 passage and valve, piston-like abutment means shiftably mounted in each ring-shaped member for riding upon the periphery of the respective circular member, a single controlling means for simultaneously actuating the valves in said two circular members, and cam means for operating said controlling meansf 3. In a hydraulic clutch and brake` mechanism a rotary shaft, two substantially circular mem-v bers secured in aligned and spaced relation to said shaft, each of said members embodying channel-like recesses in its periphery, a passage connecting said recesses, and a valve controlling said passage, a ring-shaped member for each of said circular members eccentrically encircling same andforming an endless fluid channel including said recesses, passage and valve, pistonlike abutment means shiftably mounted in each K ring-shaped member for riding upon the'periphery of the respectivecircular member and bridging said recesses, a rotatable shaft between said two circular members coupled with the valves in said passages, lever means slidably and non-rotatably secured to said rotatable shaft, and cam means co-operating with said lever means in controlling said valves by rotating said rotatable shaft.

4. In a hydraulic clutch and brake mechanism a rotary shaft, an inner membersecured to said shaft for rotation therewith, an outer member encircling said inner member and forming a crescent-shaped working chamber therewith, abutment means carried by one of said members and subdividing said chamber into compartments, a passage connecting said compartments, a valve in said passage, a 'second inner member secured to said shaft in spaced 'relation with respect to said first inner member, a lstationary outer member encircling said second inner member and forming asecond crescent-shaped Working chamber therewith, abutment means carried by one of said stationary outer member and/or said second inner member for subdividing said second chamber into compartments, a passage connecting said last compartments, a valve controlling said last named. passage, and controlling means for actuating both of said valves in timedrelation with respect to each other.

5. A hydraulic clutch' and brake mechanism for controlling the rotation of a shaft comprising` a clutch "member coupled with said shaftand a brake member co-operating with said clutch member and coupled with said shaft, said 'clutch and brake members eachv embodying inner members rigidly secured to said shaft in spaced rela tion with .respect to each other, outer members encircling said inner members and forming crescent-shaped working chambers therewith, abutment means subdividing each of said working chambers into compartments, passage means in said inner members interconnecting the respective inner compartments, and valve means in said passage means, and means coupled with said valve means for controlling same in timed relation with respect to each other.

6. A hydraulic clutch and brake mechanism as described in claim- 5, embodying means for rigidly mounting the outer member of said brake member. L

7.A hydraulic clutch and brake mechanism comprising a hydraulic clutch, a hydraulic brake,

a rotary shaft supporting said clutch and brake and actuated thereby, and means for engaging and disengaging in sequence said clutch and brake with said shaft, said hydraulic brake embodying a circular inner member, a larger outer member sleeved upon said inner member in axially offset relation with respect thereto, soas to contact at one side therewith and to form a crescent-shaped working chamber between said two members, said two members being rotatable with respect to each other, a valve chamber in said inner member, oppositely arranged channellike recesses in the periphery of said inner member in open communication with said valve chamber to form a substantially circuitous passage between said twowmembers, valve means in said valve chamber, and yieldingly -shiftable means carried by said outer member and extending into said working chamber for yielding contact with the periphery of said inner member, said shiftable means being adapted to circulate a fluid in said passage to and through said valve chamber, and absorb shock-like braking action by' too sudden operation of said valve when said members rotate With respect to each other.

8. A hydraulic clutch `and brake mechanism comprising a hydraulic clutch, a hydraulic brake, a rotary shaft supporting said clutch and brake and actuated thereby, and means for engaging and disengaging in sequence said clutch and brake with said shaft, said hydraulic brake embodying a circular inner member having symmetrically arranged channel-like recesses in its periphery, a Valve chamber between and connecting said recesses, a valve in said valve chamber, an outer member encircling said inner member and forming an endless fluid channel therewith,

said members being rotatable with respect to each other and said valve controlling the circulation of iiuid in said channel, and means radially shiftably arranged Within said outer member and extending into` said endless channel and riding upon the periphery of said inner member for subdividing the said endless channel and causing circulation of the fluid therein. f

9. A hydraulic clutch and brake mechanism as -described in claim 8, having shiftable means within said outer member of said brake consisting of spring-pressed hollow pistons dimensioned to closely fit-the width of said chamber, so as to subdivide said chamber and bridge the channel- I like recesses in the periphery' of said inner member when riding on said periphery, and effect a shock absorbing action during abrupt closing of said valve.

10. A hydraulic clutch and brake mechanism comprising a hydraulic clutch, a hydraulic brake, a rotary shaft supporting said clutch and brake and actuated thereby, and means for engaging and disengaging in sequence said clutch and brake with said shaft, said hydraulic brake comprising an inner member of substantially cylindrical form, a rotatable Valve mounted in said inner member, parallel to the axis thereof, channel-like recesses ofF substantial length in the periphery of said inner member 'at opposite sides of said valve and in 'communication therewith, an outer member sleeved upon said inner member in axially offset relation .thereto for forming an endless passage including said recesses and controlled by said valve, and yielding means shiftably mounted in said outer member for riding uponsaid inner member and bridging the vrecesses therein, said yielding means circulating the uid in said passage without interfering with the valve in said inner member.

11. A hydraulic clutch and brake mechanism comprising a hydraulic clutch, a hydraulic brake, and a rotary shaft supporting said clutch and said clutch and brake each em lcom actuated thereby. and means for engaging and disengaging in sequence said clutch and brake with said shaft, said hydraulic brake comprising a circular inner member, substans tially oppositelyarranged channel-like recesses of substantial length in a portion of the periphery of said chamber, a valve chamber in said member having inlet and outlet passages communicating with said channels, a valve in said valve chamber, and an outer member encircling said inner member in axially offset relation with respect thereto, said inner and outer members being rotatable with respect to each other and forming a circular fluid passage including said valve chamber and valve, and shiftable means carried by said outer member and adapted to ride uponv the periphery of said inner member and bridge said channel-like recesses to effect circulation of uid in said circular passage when said inner and outer members rotate with respect to each other.

12. A hydraulic clutch and brake mechanism comprising a hydraulic clutch; a hydraulic brake: g a substaninner member having oppositely arranged passages communicating with a valve chamber with a valve in said chamber, an outer member eccentrically encircling said inner member for forming an endless fluid channel including said passages and valve chamber, and yielding means shiftably mounted in said outer member and riding upon the periphery of the inner member: members of said clutch and brake with each other in a mannerthat their valves are axially aligned. a

13. A hydraulic` clutch and brake mechanism as described in claim 12, wherein means are provided for jointly actuating the aligned valves of said clutch and said brake.

- 14. A hydraulic clutch and brake mechanism comprising a hydraulic clutch, a hydraulic brake, a rotary shaft supporting said clutch and brake and actuated thereby, and means for engaging and disengaging in sequence' brake and tially circular said clutch and brake with, said shaft, said hydraulic clutchlemby bodying a valved an outer member, said members forming an endless valvecontrolled duid passage, piston-like abutment means shiitably mounted in said outer riding upon the periphery of said inner member j for circulating uid in said endless passage, and

means in said outer member counteracting centrifugal forces on said abutment means during rotation of said outer member.

15. A hydraulic clutch and g a hydraulic clutch, a hydraulic brake, a rotary shaft supporting said clutch and actuated thereby, and means for engaging and disengaging in sequence said clutch and brake with said shaft. said hydraulic clutch embodying a substantially circular inner a valved passage in said member and a valve controlling said passage,l an outer member eccentricaily encircling said iluid channel including said valved ge and controlled by said valve, piston-like abutment means sniftabiy mounted in said cuter member for lriding upon the and means rigidly connecting the inner member,

inner member for forming periphery of said inner member, and means counteracting cen1 trifugal forces on said abutment means during rotation of said outer member.

16. A clutch and brake mechanism as described in claim 15, wherein saidouter member of said clutch embodies a ring-shaped chamber nlled with liquid, wherein said abutment means extend into said ring-shaped chamber, and wherein said counteracting means embody piston means shiftably extended into said ring-shaped chamber andv dimensioned to 'eiiect increase of the pressure of theliquid in said chamber centrifugal force acting on said abutment means.

1'1. A hydraulic clutch and as described in claim 14, wherein said outerv member of said clutch is chambered and filled with liquid, wherein said abutment means slidably extendA into the liquid filled chamber of said outer member, and wherein said counteracting means embody members slidably extended into said liquid lled chamber of said outer niember for increasing the pressure of liquid in said chamber substantially proportionate to the centrifugal force acting on said abutment means.

18. A hydraulic clutch and as described in claim member of said clutch is chambered and filled with liquid, wherein said abutment means slidably extend into the liquid filled chamber of said outer member, and wherein said counteracting means embody members slidably guided in re cessed bosses in the liquid illled'v chamber of said outer member, which bosses communicate with i the endless f iuid passage of said-hydraulic member for eiecting coupling with shock absorbing action between said outer and inner members.

A clutch and brake mechanism as described in claim 14, wherein said outer member o! said clutch is liquid, wherein said abutment means slidably extend into the liquid filled chamber of said outer member, wherein said counteracting means embody members slidably guided in recessed bosses in the liquid filled chamber, municate with the endless fluid passage of said draulic member for effecting coupling with shock absorbing action between' said outer and inner members, and wherein pressure actuated control means are provided in said liquid chamber to control the power for driving said outer aid hydraulic member.

20. In a hydraulic clutch and brake mechanism a hydraulic clutch, a hydraulic shaft supporting said clutch and brake and actuated thereby, and means for engaging and disengaging in sequence fsaid' clutch and brake with said shaft, said hydraulic clutch embodying a substantially circular inner member, a valved passage in said member and a valve controlling said passage, an outer member eccentrically en,

periphery of said inner member, and means counter-acting centrifugal' forces on said abutment means during rotation of said outer member.

MARTIN which bosses com.

brake, a rotary 

